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Test Bench - Amplified Piezoelectric Actuator

Table of Contents

This document is divided in the following sections:

1 Experimental Setup

A schematic of the test-bench is shown in Figure 1.

A mass can be vertically moved using the amplified piezoelectric actuator (APA95ML). The displacement of the mass (relative to the mechanical frame) is measured by the interferometer.

The APA95ML has three stacks that can be used as actuator or as sensors.

Pictures of the test bench are shown in Figure 2 and 3.

test_bench_apa_schematic.png

Figure 1: Schematic of the Setup

setup_picture.png

Figure 2: Picture of the Setup

setup_zoom.png

Figure 3: Zoom on the APA

Here are the equipment used in the test bench:

  • Attocube interferometer (doc)
  • Cedrat Amplified Piezoelectric Actuator APA95ML (doc)
  • Voltage Amplifier LA75B (doc)
  • Speedgoat IO131 with 16bits ADC and DAC (doc)
  • Low Noise Voltage Preamplifier from Ametek (doc)

2 Estimation of electrical/mechanical relationships

In order to correctly model the piezoelectric actuator with Simscape, we need to determine:

  1. \(g_a\): the ratio of the generated force \(F_a\) to the supply voltage \(V_a\) across the piezoelectric stack
  2. \(g_s\): the ratio of the generated voltage \(V_s\) across the piezoelectric stack when subject to a strain \(\Delta h\)

We estimate \(g_a\) and \(g_s\) using different approaches:

  1. Section 2.1: \(g_a\) is estimated from the datasheet of the piezoelectric stack
  2. Section 2: \(g_a\) and \(g_s\) are estimated using the piezoelectric constants
  3. Section 2.3: \(g_a\) and \(g_s\) are estimated experimentally

2.1 Estimation from Data-sheet

The stack parameters taken from the data-sheet are shown in Table 1.

Table 1: Stack Parameters
Parameter Unit Value
Nominal Stroke \(\mu m\) 20
Blocked force \(N\) 4700
Stiffness \(N/\mu m\) 235
Voltage Range \(V\) -20..150
Capacitance \(\mu F\) 4.4
Length \(mm\) 20
Stack Area \(mm^2\) 10x10

Let’s compute the generated force

The stroke is \(L_{\max} = 20\mu m\) for a voltage range of \(V_{\max} = 170 V\). Furthermore, the stiffness is \(k_a = 235 \cdot 10^6 N/m\).

The relation between the applied voltage and the generated force can be estimated as follows:

\begin{equation} g_a = k_a \frac{L_{\max}}{V_{\max}} \end{equation}
ka = 235e6; % [N/m]
Lmax = 20e-6; % [m]
Vmax = 170; % [V]
ga = ka*Lmax/Vmax; % [N/V]
ga = 27.6 [N/V]

From the parameters of the stack, it seems not possible to estimate the relation between the strain and the generated voltage.

2.2 Estimation from Piezoelectric parameters

In order to make the conversion from applied voltage to generated force or from the strain to the generated voltage, we need to defined some parameters corresponding to the piezoelectric material:

d33 = 300e-12; % Strain constant [m/V]
n   = 80;      % Number of layers per stack
ka  = 235e6;   % Stack stiffness [N/m]

The ratio of the developed force to applied voltage is:

\begin{equation} \label{org6f1476c} F_a = g_a V_a, \quad g_a = d_{33} n k_a \end{equation}

where:

  • \(F_a\): developed force in [N]
  • \(n\): number of layers of the actuator stack
  • \(d_{33}\): strain constant in [m/V]
  • \(k_a\): actuator stack stiffness in [N/m]
  • \(V_a\): applied voltage in [V]

If we take the numerical values, we obtain:

ga = d33*n*ka; % [N/V]
ga = 5.6 [N/V]

From (Fleming and Leang 2014) (page 123), the relation between relative displacement of the sensor stack and generated voltage is:

\begin{equation} \label{org43f15ff} V_s = \frac{d_{33}}{\epsilon^T s^D n} \Delta h \end{equation}

where:

  • \(V_s\): measured voltage in [V]
  • \(d_{33}\): strain constant in [m/V]
  • \(\epsilon^T\): permittivity under constant stress in [F/m]
  • \(s^D\): elastic compliance under constant electric displacement in [m^2/N]
  • \(n\): number of layers of the sensor stack
  • \(\Delta h\): relative displacement in [m]

If we take the numerical values, we obtain:

d33 = 300e-12; % Strain constant [m/V]
n   = 80;      % Number of layers per stack
eT  = 5.3e-9;  % Permittivity under constant stress [F/m]
sD  = 2e-11;   % Compliance under constant electric displacement [m2/N]
gs = d33/(eT*sD*n); % [V/m]
gs = 35.4 [V/um]

2.3 Estimation from Experiment

The idea here is to obtain the parameters \(g_a\) and \(g_s\) from the comparison of an experimental identification and the identification using Simscape.

Using the experimental identification, we can easily obtain the gain from the applied voltage to the generated displacement, but not to the generated force. However, from the Simscape model, we can easily have the link from the generated force to the displacement, them we can computed \(g_a\).

Similarly, it is fairly easy to experimentally obtain the gain from the stack displacement to the generated voltage across the stack. To link that to the strain of the sensor stack, the simscape model is used.

2.3.1 From actuator voltage \(V_a\) to actuator force \(F_a\)

The data from the identification test is loaded.

load('apa95ml_5kg_Amp_E505.mat', 't', 'um', 'y');

% Any offset value is removed:
um = detrend(um, 0); % Amplifier Input Voltage [V]
y  = detrend(y , 0); % Mass displacement [m]

Now we add a factor 10 to take into account the gain of the voltage amplifier and thus obtain the voltage across the piezoelectric stack.

um = 10*um; % Stack Actuator Input Voltage [V]

Then, the transfer function from the stack voltage to the vertical displacement is computed.

Ts = t(end)/(length(t)-1);
Fs = 1/Ts;

win = hanning(ceil(1*Fs));

[tf_est, f] = tfestimate(um, y, win, [], [], 1/Ts);

The gain from input voltage of the stack to the vertical displacement is determined:

g_d_Va = 4e-7; % [m/V]

gain_Va_to_d.png

Figure 4: Transfer function from actuator stack voltage \(V_a\) to vertical displacement of the mass \(d\)

Then, the transfer function from forces applied by the stack actuator to the vertical displacement of the mass is identified from the Simscape model.

m = 5.5;

%% Name of the Simulink File
mdl = 'piezo_amplified_3d';

%% Input/Output definition
clear io; io_i = 1;
io(io_i) = linio([mdl, '/Fa'], 1, 'openinput');  io_i = io_i + 1; % Actuator Force [N]
io(io_i) = linio([mdl, '/y'],  1, 'openoutput'); io_i = io_i + 1; % Vertical Displacement [m]

Gd = linearize(mdl, io);

The DC gain the the identified dynamics

g_d_Fa = abs(dcgain(Gd)); % [m/N]
G_d_Fa = 1.2e-08 [m/N]

And finally, the gain \(g_a\) from the the actuator voltage \(V_a\) to the generated force \(F_a\) can be computed:

\begin{equation} g_a = \frac{F_a}{V_a} = \frac{F_a}{d} \frac{d}{V_a} \end{equation}
ga = g_d_Va/g_d_Fa;
ga = 33.7 [N/V]

The obtained comparison between the Simscape model and the identified dynamics is shown in Figure 5.

compare_Gd_id_simscape.png

Figure 5: Comparison of the identified transfer function between actuator voltage \(V_a\) and vertical mass displacement \(d\)

2.3.2 From stack strain \(\Delta h\) to generated voltage \(V_s\)

Now, the gain from the stack strain \(\Delta h\) to the generated voltage \(V_s\) is estimated.

We can determine the gain from actuator voltage \(V_a\) to sensor voltage \(V_s\) thanks to the identification. Using the simscape model, we can have the transfer function from the actuator voltage \(V_a\) (using the previously estimated gain \(g_a\)) to the sensor stack strain \(\Delta h\).

Finally, using these two values, we can compute the gain \(g_s\) from the stack strain \(\Delta h\) to the generated Voltage \(V_s\).

Identification data is loaded.

load('apa95ml_5kg_2a_1s.mat', 't', 'u', 'v');

u = detrend(u, 0); % Input Voltage of the Amplifier [V]
v = detrend(v, 0); % Voltage accross the stack sensor [V]

Here, an amplifier with a gain of 20 is used.

u = 20*u; % Input Voltage of the Amplifier [V]

Then, the transfer function from \(V_a\) to \(V_s\) is identified and its DC gain is estimated (Figure 6).

Ts = t(end)/(length(t)-1);
Fs = 1/Ts;

win = hann(ceil(10/Ts));

[tf_est, f] = tfestimate(u, v, win, [], [], 1/Ts);
g_Vs_Va = 0.022; % [V/V]

gain_Va_to_Vs.png

Figure 6: Transfer function from actuator stack voltage \(V_a\) to sensor stack voltage \(V_s\)

Now the transfer function from the actuator stack voltage to the sensor stack strain is estimated using the Simscape model.

m = 5.5;

%% Name of the Simulink File
mdl = 'piezo_amplified_3d';

%% Input/Output definition
clear io; io_i = 1;
io(io_i) = linio([mdl, '/Va'], 1, 'openinput');  io_i = io_i + 1; % Actuator Voltage [V]
io(io_i) = linio([mdl, '/dL'], 1, 'openoutput'); io_i = io_i + 1; % Sensor Stack displacement [m]

Gf = linearize(mdl, io);

The gain from the actuator stack voltage to the sensor stack strain is estimated below.

G_dh_Va = abs(dcgain(Gf));
G_dh_Va = 6.2e-09 [m/V]

And finally, the gain \(g_s\) from the sensor stack strain to the generated voltage can be estimated:

\begin{equation} g_s = \frac{V_s}{\Delta h} = \frac{V_s}{V_a} \frac{V_a}{\Delta h} \end{equation}
gs = g_Vs_Va/G_dh_Va; % [V/m]
gs = 3.5 [V/um]

compare_Gf_id_simscape.png

Figure 7: Comparison of the identified transfer function between actuator voltage \(V_a\) and sensor stack voltage

2.4 Conclusion

The obtained parameters \(g_a\) and \(g_s\) are not consistent between the different methods.

The one using the experimental data are saved and further used.

save('./matlab/mat/apa95ml_params.mat', 'ga', 'gs');

3 Simscape model of the test-bench

The idea here is to model the test-bench using Simscape.

Whereas the suspended mass and metrology frame can be considered as rigid bodies in the frequency range of interest, the Amplified Piezoelectric Actuator (APA) is flexible.

To model the APA, a Finite Element Model (FEM) is used (Figure 8) and imported into Simscape.

APA95ML_FEM.png

Figure 8: Finite Element Model of the APA95ML

3.1 Import Mass Matrix, Stiffness Matrix, and Interface Nodes Coordinates

We first extract the stiffness and mass matrices.

K = readmatrix('APA95ML_K.CSV');
M = readmatrix('APA95ML_M.CSV');
Table 2: First 10x10 elements of the Stiffness matrix
300000000.0 -1000.0 -30000.0 -40.0 70000.0 300.0 20000000.0 -30.0 -5000.0 5
-1000.0 50000000.0 -7000.0 800000.0 -20.0 300.0 3000.0 5000000.0 400.0 -40000.0
-30000.0 -7000.0 100000000.0 -200.0 -60.0 70.0 3000.0 3000.0 -8000000.0 -30.0
-40.0 800000.0 -200.0 20000.0 -0.4 4 30.0 40000.0 7 -300.0
70000.0 -20.0 -60.0 -0.4 3000.0 1 -6000.0 10.0 8 -0.1
300.0 300.0 70.0 4 1 40000.0 -10.0 -10.0 30.0 0.1
20000000.0 3000.0 3000.0 30.0 -6000.0 -10.0 300000000.0 2000.0 9000.0 -100.0
-30.0 5000000.0 3000.0 40000.0 10.0 -10.0 2000.0 50000000.0 -3000.0 -800000.0
-5000.0 400.0 -8000000.0 7 8 30.0 9000.0 -3000.0 100000000.0 100.0
5 -40000.0 -30.0 -300.0 -0.1 0.1 -100.0 -800000.0 100.0 20000.0
Table 3: First 10x10 elements of the Mass matrix
0.03 7e-08 2e-06 -3e-09 -0.0002 -6e-08 -0.001 8e-07 6e-07 -8e-09
7e-08 0.02 -1e-06 9e-05 -3e-09 -4e-09 -1e-06 -0.0006 -4e-08 5e-06
2e-06 -1e-06 0.02 -3e-08 -4e-08 1e-08 1e-07 -2e-07 0.0003 1e-09
-3e-09 9e-05 -3e-08 1e-06 -3e-11 -3e-13 -7e-09 -5e-06 -3e-10 3e-08
-0.0002 -3e-09 -4e-08 -3e-11 2e-06 6e-10 2e-06 -7e-09 -2e-09 7e-11
-6e-08 -4e-09 1e-08 -3e-13 6e-10 1e-06 1e-08 3e-09 -2e-09 2e-13
-0.001 -1e-06 1e-07 -7e-09 2e-06 1e-08 0.03 4e-08 -2e-06 8e-09
8e-07 -0.0006 -2e-07 -5e-06 -7e-09 3e-09 4e-08 0.02 -9e-07 -9e-05
6e-07 -4e-08 0.0003 -3e-10 -2e-09 -2e-09 -2e-06 -9e-07 0.02 2e-08
-8e-09 5e-06 1e-09 3e-08 7e-11 2e-13 8e-09 -9e-05 2e-08 1e-06

Then, we extract the coordinates of the interface nodes.

[int_xyz, int_i, n_xyz, n_i, nodes] = extractNodes('APA95ML_out_nodes_3D.txt');

The interface nodes are shown in Figure 9 and their coordinates are listed in Table 4.

Total number of Nodes 7
Number of interface Nodes 7
Number of Modes 6
Size of M and K matrices 48
Table 4: Coordinates of the interface nodes
Node i Node Number x [m] y [m] z [m]
1.0 40467.0 0.0 0.0 0.029997
2.0 40469.0 0.0 0.0 -0.029997
3.0 40470.0 -0.035 0.0 0.0
4.0 40475.0 -0.015 0.0 0.0
5.0 40476.0 -0.005 0.0 0.0
6.0 40477.0 0.015 0.0 0.0
7.0 40478.0 0.035 0.0 0.0

APA95ML_nodes_1.png

Figure 9: Interface Nodes chosen for the APA95ML

Using K, M and int_xyz, we can use the Reduced Order Flexible Solid simscape block.

3.2 Simscape Model

The flexible element is imported using the Reduced Order Flexible Solid Simscape block.

To model the actuator, an Internal Force block is added between the nodes 3 and 12. A Relative Motion Sensor block is added between the nodes 1 and 2 to measure the displacement and the amplified piezo.

One mass is fixed at one end of the piezo-electric stack actuator, the other end is fixed to the world frame.

m = 5.5;
load('apa95ml_params.mat', 'ga', 'gs');

3.3 Dynamics from Actuator Voltage to Vertical Mass Displacement

The identified dynamics is shown in Figure 10.

%% Name of the Simulink File
mdl = 'piezo_amplified_3d';

%% Input/Output definition
clear io; io_i = 1;
io(io_i) = linio([mdl, '/Va'], 1, 'openinput');  io_i = io_i + 1; % Actuator Voltage [V]
io(io_i) = linio([mdl, '/y'],  1, 'openoutput'); io_i = io_i + 1; % Vertical Displacement [m]

Ghm = linearize(mdl, io);

dynamics_act_disp_comp_mass.png

Figure 10: Dynamics from \(F\) to \(d\) without a payload and with a 5kg payload

3.4 Dynamics from Actuator Voltage to Force Sensor Voltage

The obtained dynamics is shown in Figure 11.

%% Name of the Simulink File
mdl = 'piezo_amplified_3d';

%% Input/Output definition
clear io; io_i = 1;
io(io_i) = linio([mdl, '/Va'], 1, 'openinput');  io_i = io_i + 1; % Voltage Actuator [V]
io(io_i) = linio([mdl, '/Vs'], 1, 'openoutput'); io_i = io_i + 1; % Sensor Voltage [V]

Gfm = linearize(mdl, io);

dynamics_force_force_sensor_comp_mass.png

Figure 11: Dynamics from \(F\) to \(F_m\) for \(m=0\) and \(m = 10kg\)

3.5 Save Data for further use

save('matlab/mat/fem_simscape_models.mat', 'Ghm', 'Gfm')

4 Measurement of the ambient noise in the system

This first measurement consist of measuring the displacement of the mass using the interferometer when no voltage is applied to the actuator.

This can help determining the actuator voltage necessary to generate a motion way above the measured noise and disturbances, and thus obtain a good identification.

4.1 Time Domain Data

huddle_test_time_domain.png

Figure 12: Measurement of the Mass displacement during Huddle Test

4.2 PSD of Measurement Noise

Ts = t(end)/(length(t)-1);
Fs = 1/Ts;

win = hanning(ceil(1*Fs));
[pxx, f] = pwelch(y(1000:end), win, [], [], Fs);

huddle_test_pdf.png

Figure 13: Amplitude Spectral Density of the Displacement during Huddle Test

5 Identification of the dynamics from actuator Voltage to displacement

The setup used for the identification of the dynamics from \(V_a\) to \(d\) is shown in Figure 14.

A Voltage amplifier with a gain of \(10\) is used. Two stacks are used as actuators while one stack is used as a force sensor.

test_bench_apa_identification.png

Figure 14: Test Bench used for the identification of the dynaimcs from \(V_a\) to \(d\)

5.1 Load Data

The data from the “noise test” and the identification test are loaded.

ht = load('huddle_test.mat', 't', 'u', 'y');
load('apa95ml_5kg_Amp_E505.mat', 't', 'um', 'y');

Any offset value is removed:

um = detrend(um, 0); % Input Voltage [V]
y  = detrend(y , 0); % Mass displacement [m]

ht.u  = detrend(ht.u, 0);
ht.y  = detrend(ht.y, 0);

Now we add a factor 10 to take into account the gain of the voltage amplifier.

um   = 10*um;

5.2 Comparison of the PSD with Huddle Test

Ts = t(end)/(length(t)-1);
Fs = 1/Ts;

win = hanning(ceil(1*Fs));
[pxx, f] = pwelch(y, win, [], [], Fs);
[pht, ~] = pwelch(ht.y, win, [], [], Fs);

apa95ml_5kg_PI_pdf_comp_huddle.png

Figure 15: Comparison of the ASD for the identification test and the huddle test

5.3 Compute TF estimate and Coherence

[tf_est, f] = tfestimate(um, -y, win, [], [], 1/Ts);
[co_est, ~] = mscohere(  um, -y, win, [], [], 1/Ts);

apa95ml_5kg_PI_coh.png

Figure 16: Coherence

Comparison with the FEM model

load('mat/fem_simscape_models.mat', 'Ghm');

apa95ml_5kg_pi_comp_fem.png

Figure 17: Comparison of the identified transfer function and the one estimated from the FE model

6 Identification of the dynamics from actuator Voltage to force sensor Voltage

The same setup shown in Figure 14 is used.

The data are loaded:

load('apa95ml_5kg_2a_1s.mat', 't', 'u', 'v');

Any offset is removed.

u = detrend(u, 0); % Speedgoat DAC output Voltage [V]
v = detrend(v, 0); % Speedgoat ADC input Voltage (sensor stack) [V]

Here, the amplifier gain is 20.

u = 20*u; % Actuator Stack Voltage [V]

The transfer function from the actuator voltage \(V_a\) to the force sensor stack voltage \(V_s\) is computed.

Ts = t(end)/(length(t)-1);
Fs = 1/Ts;

win = hann(ceil(5/Ts));

[tf_est,  f] = tfestimate(u, v, win, [], [], 1/Ts);
[coh,     ~] = mscohere(  u, v, win, [], [], 1/Ts);

The coherence is shown in Figure 18.

apa95ml_5kg_cedrat_coh.png

Figure 18: Coherence

The Simscape model is loaded and compared with the identified dynamics in Figure 19. The non-minimum phase zero is just a side effect of the not so great identification. Taking longer measurements would results in a minimum phase zero.

load('mat/fem_simscape_models.mat', 'Gfm');

bode_plot_force_sensor_voltage_comp_fem.png

Figure 19: Comparison of the identified dynamics from voltage output to voltage input and the FEM

7 Integral Force Feedback

test_bench_apa_schematic_iff.png

Figure 20: Schematic of the test bench using IFF

7.1 IFF Plant

From the identified plant, a model of the transfer function from the actuator stack voltage to the force sensor generated voltage is developed.

w_z = 2*pi*111; % Zeros frequency [rad/s]
w_p = 2*pi*255; % Pole frequency [rad/s]
xi_z = 0.05;
xi_p = 0.015;
G_inf = 0.1;

Gi = G_inf*(s^2 + 2*xi_z*w_z*s + w_z^2)/(s^2 + 2*xi_p*w_p*s + w_p^2);

Its bode plot is shown in Figure 21.

iff_plant_identification_apa95ml.png

Figure 21: Bode plot of the IFF plant

The controller used in the Integral Force Feedback Architecture is:

\begin{equation} K_{\text{IFF}}(s) = \frac{g}{s + 2\cdot 2\pi} \cdot \frac{s}{s + 0.5 \cdot 2\pi} \end{equation}

where \(g\) is a gain that can be tuned.

Above 2 Hz the controller is basically an integrator, whereas an high pass filter is added at 0.5Hz to further reduce the low frequency gain.

In the frequency band of interest, this controller should mostly act as a pure integrator.

The Root Locus corresponding to this controller is shown in Figure 22.

root_locus_iff_apa95ml_identification.png

Figure 22: Root Locus for IFF

7.2 First tests with few gains

The controller is now implemented in practice, and few controller gains are tested: \(g = 0\), \(g = 10\) and \(g = 100\).

For each controller gain, the identification shown in Figure 20 is performed.

iff_g10  = load('apa95ml_iff_g10_res.mat',  'u', 't', 'y', 'v');
iff_g100 = load('apa95ml_iff_g100_res.mat', 'u', 't', 'y', 'v');
iff_of   = load('apa95ml_iff_off_res.mat',  'u', 't', 'y', 'v');
Ts = 1e-4;
win = hann(ceil(10/Ts));

[tf_iff_g10, f] = tfestimate(iff_g10.u, iff_g10.y, win, [], [], 1/Ts);
[co_iff_g10, ~] = mscohere(iff_g10.u, iff_g10.y, win, [], [], 1/Ts);

[tf_iff_g100, ~] = tfestimate(iff_g100.u, iff_g100.y, win, [], [], 1/Ts);
[co_iff_g100, ~] = mscohere(iff_g100.u, iff_g100.y, win, [], [], 1/Ts);

[tf_iff_of, ~] = tfestimate(iff_of.u, iff_of.y, win, [], [], 1/Ts);
[co_iff_of, ~] = mscohere(iff_of.u, iff_of.y, win, [], [], 1/Ts);

The coherence between the excitation signal and the mass displacement as measured by the interferometer is shown in Figure 23.

iff_first_test_coherence.png

Figure 23: Coherence

The obtained transfer functions are shown in Figure 24. It is clear that the IFF architecture can actively damp the main resonance of the system.

iff_first_test_bode_plot.png

Figure 24: Bode plot for different values of IFF gain

7.3 Second test with many Gains

Then, the same identification test is performed for many more gains.

load('apa95ml_iff_test.mat', 'results');
Ts = 1e-4;
win = hann(ceil(10/Ts));
tf_iff = {zeros(1, length(results))};
co_iff = {zeros(1, length(results))};
g_iff = [0, 1, 5, 10, 50, 100];

for i=1:length(results)
    [tf_est, f] = tfestimate(results{i}.u, results{i}.y, win, [], [], 1/Ts);
    [co_est, ~] = mscohere(results{i}.u, results{i}.y, win, [], [], 1/Ts);

    tf_iff(i) = {tf_est};
    co_iff(i) = {co_est};
end

The obtained dynamics are shown in Figure 25.

iff_results_bode_plots.png

Figure 25: Identified dynamics from excitation voltage to the mass displacement

For each gain, the parameters of a second order resonant system that best fits the data are estimated and are compared with the data in Figure 26.

G_id = {zeros(1,length(results))};

f_start = 70; % [Hz]
f_end = 500; % [Hz]

for i = 1:length(results)
    tf_id = tf_iff{i}(sum(f<f_start):length(f)-sum(f>f_end));
    f_id = f(sum(f<f_start):length(f)-sum(f>f_end));

    gfr = idfrd(tf_id, 2*pi*f_id, Ts);
    G_id(i) = {procest(gfr,'P2UDZ')};
end

iff_results_bode_plots_identification.png

Figure 26: Comparison of the measured dynamic and the identified 2nd order resonant systems that best fits the data

Finally, we can represent the position of the poles of the 2nd order systems on the Root Locus plot (Figure 27).

iff_results_root_locus.png

Figure 27: Root Locus plot of the identified IFF plant as well as the identified poles of the damped system

Bibliography

Fleming, Andrew J., and Kam K. Leang. 2014. Design, Modeling and Control of Nanopositioning Systems. Advances in Industrial Control. Springer International Publishing. https://doi.org/10.1007/978-3-319-06617-2.

Author: Dehaeze Thomas

Created: 2020-11-24 mar. 18:24